Slitting mechanism for endless web material



SLITTING MECHANISM FOR ENDLESS WEB MATERIAL 3 Sheets-Sheet 1 Filed June5, 1963 UN 5m WM: win 6x c gm fun Ma m A W\ Mw m -\m m. m o. u in |MJ my 25, 1965 w. G. PRINTZ ETAL 3,185,010

SLITTING MECHANISM FOR ENDLESS WEB MATERIAL Filed June 3, 1963 3Sheets-Sheet 2 INVENTORS, IVA/WE/VGPe/NTZ D/M/TE/JS UBE/V/5 MAL/4M[/THGO MEL b0 Y-Ioczs "MOIQNEY 1965 w. s. PRINTZ ETAL 3,185,010

SLITTING MECHANISM FOR ENDLESS WEB MATERIAL Filed June 3, 1963Sheets-Sheet 3 I m 84 4% a 1os- 1 m 4- 10awe, 5: as gas \40 F 6 5 V56) Il '10 P w 5615 '4 use x x I65 v14, A60

as n4 m1 INVENTORS,

MEEE/V 6. Fem/r2 DIM/TEA/S Fuse/W5 MLL MM 1/77/60 BY MEL U). FLOCKSATTORNEY United States Patent 3,185,010 SLITTING MECHANISM FOR ENDLESSWEB MATERIAL Warren G. Printz, Middletow-n, Dimitrijs Rubenis,

Monroe, and William Lithgo, Middletown, Ohio, as-

signors to Diamond International Corporation, a corporation of DelawareFiled .l'une 3, 1963, Ser. No. 284,915 14 Claims. (Cl. 83-482) Thepresent invention relates generally to slitting apparatus, and moreparticularly, to the type of slitting apparatus of the characterdisclosed, for example, in Us. Letters Patent to Clem No. 2,571,20l,issued October 16, 195 1, employed in the slitting of webs of paperwebs.

The improved slitting apparatus of this invention is of the narrow-cut,shear type such as that used to trim and cut web material on web windingmachines, for example.

This type of slitting apparatus is generally in the form of a thin steeldisc of about 6 to 8 inches in diameter, manufactured from hardened andtempered tool steel, and peripherally ground to obtain a sharp edge inorder to form a circular knife. The steel disc cooperates with anunderlying driven cutter disc or drum, and will be kept in rotatingcontact, i.e., by overlapping and engaging the side of the drum, and theplane of the axis of rotation thereof will be at a slight angle withrespect to the axis, of rotation of the cooperating drum to form a shearangle similar in effect to the angle of contact of two cooperating andoverlapping blades of a pair of scissors. Just as in a pair of scissors,the blade and drum, while rotating together, must be maintained incontact at an optimum amount of pressure in order to sever a web ofmaterial with a consistently clean cut.

The necessity for maintaining the optimum shear angle and optimumpressure is well recognized by the prior art, and various means havebeen devised, the more common of which being through the utilization ofa spring pressure.

A primary object of the present invention is to use fluid pressure,preferably pneumatic pressure, in conjunction with means whereby thepressure may be readily controlled at a remote control console, and thispressure may be readily adjusted to suit slitting requirements fordifferent grades of material being processed.

A further object of the present invention is to provide improved webslitting apparatus which includes means for applying pressure tonormally retain an upper cutter disc and bottom cutting drum in spacedrelation; which utilizes fluid pressure to force the blades inengagement by means of a compound movement whereby engagement anddisengagement of the cooperating cutting blades is such a movement thatsubstantially obviates damage to the blades when they are engaging anddisengaging; which affords a cam control action whereby an upper slitterblade is moved first vertically and then horizontally into engagementwith a lower slitter blade, and in which such movement is reversed; inwhich disengagement between the cooperating cutter blades issubstantially instantaneous; in which the apparatus may be readily movedon a rigid support beam and adjusted along the length thereof withoutdisturbing the previously adjusted shearing angle, overlap, and positionrelationship; and in which means are provided to readily adjust variousangular re lationships between a pair of cooperating cutter discs inorder to obtain and maintain an optimum shearing relationship.

, Other objects and the nature and advantages of the instant inventionwill be apparent from the following Patented May 25, 1965 of the upperslitter disc with a lower cutting drum;

FIG. 3 is an end elevation looking from left to right at FIG. 2, andshowing by means of phantom lines the normal angular disposition of theupper slitter disc with respect to the cooperating edge of the lowerslitter drum,

and showing by means of solid lines the normal cooperating cuttingposition between the slitter disc and slitter drum;

FIG. 4 is a view similar to FIG. 2, with portions broken away and shownin section for purposes of clarity to illustrate structural details;

FIG. 5 is an enlarged vertical section taken substantially on the planeof line 55 of FIG. 4;

FIG. 6 is an enlarged bottom plan view taken substantially on the planeof line 6--6 of FIG. 4;

FIG. 7 is an enlarged section taken substantially on the plane of line7-7 of FIG. 4; and

FIG. 8 is a further enlarged vertical section through the upper slittingdisc showing details thereof.

Referring to the drawings in detail, and first considering FIG. 1, ahorizontally extending support beam or mounting bar is indicatedgenerally at 1%, and conveniently has a dove tail cross section. Thesupport beam will be of sufficient rigidity and strength to resist theeffect of bending and torsional forces when a plurality of slittingapparatus such as that indicated generally at 12 is mounted thereon.Rotatably mounted on a suitable support shaft below the slittingapparatus 12 is a driven slitting drum or disc 14 which preferably hassuitable ground cutting edges 16 and 18 at opposite sides of an annularcircumferential rim. The two cutting edges 16 and 18 permit left orright hand installations of the upper slitting disc, and the slittingapparatus 12 includes means for adjusting or controlling the compoundmovement thereof for orientation from right to left as shown in FIGS. 3and 5, for example, or alternatively, in opposite direction, i.e., fromleft to right (not shown), as will subsequently be described in detail.

The apparatus 12 comprises a substantially rectangular body member 20including cored pocket 22 at what will be conveniently described therear portion thereof, and has extending vertically therethrough a boreportion 24; see FIG. 4. The bore portion 24 receives therethrough a bolt26 which has fixedly secured at the lower end thereof by means ofwelding 23, for example, a lower clamp block 30. It will be noted thatthe clamp block 30 has an angled lip 32 engaging a complementary portionof the mounting bar 10. The body member 20 has secured by means ofmachine screws 34 (only one shown) a mounting lip 36 having an anglededge 38 engaging on an upper complementary portion of the dove tailedmounting bar It The upper end of the bolt 26 is threaded as indicated at40 and receives thereon a washer 42 and clamp nut 44 which cooperateswith the clamp lock 30 to retain the apparatus 12 in various positionsof adjustment longitudinally of the support member 10 (a plurality ofunits 12 can be mounted on member 10).

The body member 20 has extending therethrough a vertical bore 46 whichreciprocably receives therein a guide plunger 43 preferably producedfrom a bronze or some other similar bearing-type material.

Fixedly secured in overlying relationship to the bore portion 46 is asingle-acting or double-acting fluid motor or cylinder 50 operativelyconnected to a source of fluid pressure 52.

Specific details of the fluid motor 50 are not illustrated, however, thepiston (not shown) will generally be of the single-acting, spring-returntype or double-acting type, as is conventional.

A piston rod 54 projects from the fluid motor 50 into the bore portion46 and includes a lowerthreaded portion 56 and engaged in a suitablythreaded bore portion 58 of the guide plunger. In order to relieve theaccumulation of internal pressure within the bore portion 46 above theplunger 58, a suitable relief orifice 60 is provided to communicateatmospheric pressure with the bore portion '46.

The body member 20 includes vertical guide slots 62 and 64 opening fromopposite sides of the bore portion 46, and the plunger 48 has extendingtransversely therethrough a bore portion 66 which rotatably receivestherein a mounting shaft 68, The shaft 68has journaled thereon acarriage yoke indicated generally at 70 which comprises a cam plate 72suitably apertured at 74 to receive the left hand end of shaft 68therethrough; see FIG. 4. Secured by means of suitable machine screws76'to the cam plate 72 is a mounting collar element 78 to subsequentlybe described in detail. The mounting collar 78 includes a recess 80which receives the enlarged complementary end 84=of the shaft 68therein.

The shaft '68 is suitably apertured at 86 and fixedly secured therein amounting stud 88 projecting through the slot 62 and receiving thereon awasher-spring assembly 90, and retaining nuts 92.

Operation of the fluid motor 56 results in vertical re ciprocation ofthe guide plunger 43, and comparable vertical movement of the shaft 68in guide slots 62 and 64. However, it will be noted that the cam plate72, mount- .ing collar 78 and shaft 68 are free to rotate in the boreportion '66.

Itwill be noted that the support shaft 68 defines the maintains thevertical path of movement of the cutter assembly 94 as has beenpreviously described and as is readily apparent from FIG. 4.

In order to obtain controlled oscillation of the cutter assembly 94-about the shaft 68, cam means indicated generally at 96 is provided.

The cam or control means 96 comprises a mounting block 98 secured inoverlying relationship below the bore portion 46 of the body member 20and is retained thereon by means of machine screws 1063; see FIGS. 4 and6, for example. The mounting block 98, as clearly seen in FIG. 4,includes a bore or orifice portion 102 therethrough which communicateswith the lower end of the bore portion 46 in which the plunger 48reciprocates to relieve the accumulation of pressure beneath the plunger48.

The cam plate 72; see FIG. 5, for example, includes at opposite lowerend portions thereof slightly downwardly angled cam surfaces 164 and 106which terminate in inwardly disposed arcuate portions 108 and 110,respectively. When the apparatus is in operation, only one of the camsurfacesis used, depending upon whether the cutting edge 18 of thecutting drum 14 is being used, or if the installation is reversed andthe cutting edge 16 is being used. This will be readily apparent tothose skilled in the art, in view of the structure to subsequently bedescribed in detail.

Formed on the inner surface of the cam plate 72 facing the adjacentsurface of the mounting block 98 is downwardly opening guide recess 112;see FIGS. 4-6, for example. The mounting block 98 has extendingtransversely therethrough a bore portion 114 having disposed in one endthereof a retaining ring 116 and circular sealing plate 117 and havereciprocably supported therein a guide plunger 118 subject to the forceof a compression spring 120 retained in the bore portion 114 bymeans ofa second retainer plate 121 and, retaining ring 122.

The mounting block 98 has communicating with the bore portion 114 aguide slot 124,- and the plunger 118 has mounted therein and extendingthrough' the guide slot 124 a threaded mountingshaft portion 126 uponwhich a rotatable cam follower element 128 is'mounted. Suitably mountedon a shaft. 130 is a cam follower 132 which will engage the cam edge 104of the cam plate 72 and move toward the arcuate portion 108 whenthecutter assemby 94 is in its lower-most of solid line position shownin'FIGS. 2 and 3; it will be noted that thefollower 132 does not engagethearcuate portion 198 and thus permits a range of adjustment ofpressure between cooperating cutting edges,

When, the cutter assembly 94 is inthe phantom line position, the spring120'will react against the plunger 118 which, "in turn, will reactthrough the cam follower 124 on thegroove 112 on the inner surface ofthe cam plate "to accordingly urge the campla te and cutter assemblyinto outwardly extending angular relation as clearly shown in FIG. 3.

When the fluid motor 50 is activated, and the cutter assembly 94 islowered, the camfollower 132 will engage the cam edge 104 accordinglycausing the plate 72, i.e., the cutter assembly, to move to the left orthe solid line position shown in'FIG. 3, after the blade cutting edgesoverlap, and the apparatus will be in condition for slitting webs,trimming the edge of the web, etc.

Upon relief of pressure in the fluid motor 50, which was described asbeing one-way acting fluid motor which is spring urged to an inoperativeposition; as the guide piston 48 moves to theupper phantom line positionof FIG. 2, for example, the spring12t will be effective to immediatelymove the disc cutter away from the cooperating cutting edge 18 Adouble-acting fluid motor could be used to control movements in both anoperative and inoperative-position.

It will be noted in FIG. 5, for example,-that the mounting block 98includes an aperture 134 in which the shaft 130 of the cam follower 132may be mounted foralternatively' utilizing the cutting edge 16 of thecutter drum 14 as mentioned above. The springv 120 would be inengagement with the opposite end of the guide plunger 118-for attainingthe reverse movement mentioned, and substantially instantaneous outwardmovement of the cutter assembly is aifordedwhen the fluid motor 50 isnot being activated.

The range of movement is relatively slight, i.e., the

slitter blade of the cutter assembly moving approximately A; of an inchaway from the cooperating cutting edge or" the lower slitter drum.

The showing in FIG, 3 has been exaggerated in order to emphasizeptherange of movement which. occurs when the cutter assembly 94 reaches itslowermost position.

As previously mentioned above, the carriage yoke 70 is retained on thecam plate 72 by means of screws 76, and the yoke 78 of the carriage yokeassembly is substantially G-shaped in cross-section; see FIG. 7, forexarnple, and includes a leg 136 secured in juxtaposed relation on thecam plate 72, a transverse leg 138 substantially parallel to the planeof .the slitter disc to be described, and a leg 140 parallel to leg 136.

The transverse leg 138 includes a transverse aperture 142 which hasextending therethrougha mounting nutand-bolt assembly 144 including aheaded bolt 146,,wash er 148 and clamp nut i150 receiving the threadedend of the bolt 146.

Mounted on the assembly 144 is an elongated mount ing post or bar 152,which preferably has a rectangular cross section as seen in FIG. 7. Thebar or post 152 includes an intermediate vertically extending slot 154in which a suitably conformed end 156 of the nut 150 projects.

The post 152 includes a horizontally extending lug portion 157 in whichis threadedly received a knurled abutment screw 158, the lower end ofwhich engages the upper surface of the substantially rectangularclamping nut 150; see FIGS, 1-4.

When the clamp nut and bolt assembly 144 is in a loosened condition, thescrew 158 may be rotated to vertically adjust the mounting bar or post152 with respect to the yoke 78. This adjustment will control the amountof overlap between the cutter drum 14 and the cutter disc mounted" onthe lower end of the post 152 and to be presently described.

The mounting :bar or post 152 is transversely apertured at 160 adjacentthe lower end thereof, and has mounted thereon a slitter disc assemblyindicated generally at 162. The slitter disc assembly 162 comprises amounting hub 164 including a transverse recess 166 receiving thereinroller bearing assemblies 168 which r-otatably support a mounting shaft170; see FIG. 8. A cover plate 172 is retained in overlying relationshipto the recess 166 'by means of machine screws 174 or the ike.

The shaft 170 is retained against rotation with respect to the mountingbar 152 by means of a suitable key 176, and an abutment collar 178 isdisposed opposite a clamp nut 180 threadedly engaged on the terminal endof the mounting shaft 170; which shaft projects through the transverseaperture 160 at the lower end of the mounting bar.

The hub 164 includes an annular mounting flange 182 and has oircum-posedthereabout a suitably circular slitter disc 184 retained on the flange182 in juxtaposed relation thereto by means of machine screws 186.

The peripheral cutting edge 1% of the cutter disc 184 will be inoverlapped relationship with respect to the cutting edge 18 or 16, anddue to resharpening, though the diameter of the cutting disc 184 may bereduced, the vertical adjustment provided by means of the screw 158 willcompensate for regrinding of the disc. Further, the disc 184 may bereadily removed from the mounting hub 164 by removal of the screws 186,for example.

The plane of the disc 184 is disposed at a slight angle with respect toa plane passing through the cooperating cutting edge 18 of the drum 14.Further, the axes of rotation of the cutting drum 14 and disc 184 arenot in exact alignment, i.e., the axis of rotation of the cutting disc184 slightly being advanced or leading with respect to that of the axisof rotation of the drum; see for example FIG. 2.

The so-called lead angle just mentioned is attained by means ofstructure to be presently described in detail.

The leg 136 of the yoke 78; see FIG. 7, has fixed thereon ahemispherical abutment element 1% engageable with the edge 192 of themounting bar 152.

Disposed vertically above and below a point of engagement between thehemispherical abutment element 190 and the edge 192 of the mounting bar,and mounted on the leg 140 of the yoke, is a pair of abutment screws 194and 196, the terminal ends thereof respectively engaging the edge 198 ofthe mounting bar 152.

Accordingly, when one of the screws 194 or 196 is backed off the othermay be tightened, and the longitudinal axis of the mounting bar uponwhich the cutting disc 184 is mounted may be adjusted angularly withrespect to the abut-ment element 190 which is, in a limited sense, apivotal abutment element. In this manner, the angular lead angle of thecutter disc 184 may be adjusted with respect to that of the cutter drum14; this adjustment is further made apparent when considering FIGS. l-4.

In order to adjust the shear-angle relationship of the slitter disc 184with respect to a plane passing through the cutting edge 18, forexample, the leg 138 of the yoke 78 has mounted thereon, in offsetrelationship with respect to the longitudinal axis of the mounting bar152 which passes through the axis of rotation of the slitter disc 184, apair of abutment elements having hemispherical heads 2%, see FIG. 7, inengagement with the adjacent surf-ace 262 of the mounting bar 152. The'leg 13 8 of the yoke has a pair of threaded transverse bores 204 whichreceive therein set screws 206 having hemispherical terminal ends 208 inabutting engagement with the surface 202 in spaced relation on theopposite side of the longitudinal axis of the mounting bar 152. 'It willbe noted that the aperture 142 is substantially larger than the diameterof the bolt 146 and thus when the nut and bolt assembly 144 is loosenedor backed off, the set screws 206 may be adjusted to provide therequired shear angle or angular relationship between the plane of theslitter disc and the effective cutting edge 18 or alternatively 16depending upon which type of installation is being utilized.

The adjustments referred to above, are in the nature of hundredths orthousandths of an inch, and accordingly are relatively minute. However,this slitter apparatus will afford an extremely accurate and adjustableout which is of the critical character required when slitting ortrimming huge rolls of :a continuous web of paper for newsprint, bondpaper for stationery etc.

Although only one installation of a slitter apparatus has been describedin detail, for example that used to trim the edge of a continuous web ofpaper, or paper product material, it will be readily understood that aplurality of these units may be readily adjusted longitudinally of themounting bar 10. Once the apparatus 12 has been positioned on themounting bar 10, the adjustment afforded by the screw 158, screws 194,196 and set screws 206 are accomplished. In the event the cutter disc184 has to be removed and regr-ound, this may be accomplished in arelatively simple and expeditious manner. 'After regrinding, theadjustment screw 158 may be used to lower the cutting disc 184 thenecessary amount to compensate for that material which has been groundoff during the resharpening. However, the shear angle and lead anglewill be maintained, and further adjustments thereof are independentlymade as required.

Additionally, by controlling the amount of pressure applied via thefluid motor 50, which accordingly controls vertical and subsequenthorizontal movement of the slitter assembly 94, i.e., movement of themounting bar 152 etc., the extent of horizontal movement controls thepressure between the slitter drum 14 and cutting edge 18. The movementand slitting pressure of the slitter disc will be readily determined bymeans of suitable pressure gauges provided at a remote console tocontrol the fluid motor 50. The slitter disc 184 is rotated due tofrictional engagement between the slitter drum 14 and the peripheraledge of the slitter disc 184, the drum 14 (it being understood thatthere are a plurality of these drums disposed on a suitable drive shaft)will be power rotated.

Briefly in review, the apparatus just described avoids the possibilityof damage to the cutting edges or blades while engaging and disengagingas follows:

(a) When disengaged, the slitter disc 184 is retained in its uppermostposition in the phantom line position shown in FIG. 2, and slightly toone side by virtue of the eifect of the spring (b) The fluid motor 50,which is used to force the slitter disc 184 downwardly, will not causethe cutter edge 188 to engage on the outer surface of the slitter drum14 inasmuch as the spring 129 continues to hold the disc in the phantomline position shown in FIG. 3 until the cutting edge 188 extends belowthe outer surface of the drum 14;

(0) At the end of the downward stroke or movement of the cam plate 72,the cam follower 132, which engages the cam edge 194, is effective todraw the slitter disc 184 into its adjusted shear angle relationshipwith respect to the cutting edge 18 as illustrated by solid lines inFIG. 3 and the extent of horizontal movement may be controlled;

lieved in the fluid motor 50, the slitter disc first moves horizontallyto the phantom line position shown in FIG. 3, and then. the assemblymoves vertically back to the phantom line position shown in FIG. 2;

(2) Means are provided for adjustment of the most effective shear angle,most effective lead angle, the most effective amount of pressure contactin overlap be tween the cooperating cutting edges, and means areprovided to compensate for the reduction of the slitter disc diameterdue to the regrinding;

(f) The amount of contact pressure between the cutting edges of theupper slitter disc and the lower slitter drum canbe adjusted through arange of anywhere from 2 to pounds, forexample, by means of a suitablepressure regulator in remote console which will be operatively connectedto thefluid line 52.

It will be obvious to those skilled in the art that various changes maybe made without departing from the scope of the invention and thereforethe invention is not limited to what is shown in the drawings anddescribed in the specification but only as indicated in the appendedclaims.

What is claimed is:

1. Apparatus for slitting a continuous web of material comprising asupport member, a body member mounted on said support member, firstcutter means having a circular cutting edge and mounted below said bodymember, a slitter assembly including a depending second cutter meanshaving a circular cutting edge and journaled on said slitter assembly ona fixed axis of rotation for driving,

shear-angle engagement with said first cutter means, said slitterassemblyand body member including means pivotally and reciprocablymounting said slitter assembly on said body member on an axis ofrotation above and substantially normal to the axis of rotation ofsaidfirst cutter means, fluid motor means on said body member operativelyconnected to .said slitter assembly for reciprocating said slitterassembly at said means pivotally and reciprocably mountingsaid slitterassembly and moving said second cutter means edge toward said firstcutter.

means edge, means on said slitter assembly normally urging said secondcutter means edge away from first cutter means edge and cam means onsaid body member and said slitter assembly and including cammingportions for pivoting said slitter assembly and said second cutter meansedge bodily toward and away from said first cutter means edge duringreciprocable movement of said slitter assembly during operation of saidfiuid motor means.

2. The apparatus of claim 1 in which said slitter assembly includesmounting means thereon for adjusting the relative overlap between thecutting edges of said first and second cutter means.

3. The apparatus of claim 1 in which said slitter assembly includesmeans adjustably mounting and rotating said second cutter means on anaxis substantially normal to the axis of rotation of said second cuttermeans for adjusting and maintaining the optimum shear-angle between thecutting edges of said cutter means.

4. The apparatus of claim 1 in which said slitter assembly includesadjusting means for orienting the axis of rotation of said second cuttermeans out of vertical alignment with the axis of rotation of said firstcutter means.

5. The apparatus of claim 1 in which said body member includes a guideelement connected to said fluid motor means and reciprocably mountedtherein, said guide element including a shaft journaled therein andextending transversely of said body member, said shaft element beingterminally and pivotally connected to said slitter assembly.

6. The structure of claim 1 in which said slitter assembly includes acam plate disposed at one side of said body member, said cam meanscomprising a cam element on said body member, projecting laterally fromsaid one &

side of'said body member at which said cam plateis dis posed, said camplate including a cam edge portion engageable with said cam followerelement during recipro- Cation of said slitter assembly and controllingrelative horizontal movement of said cutter means with respect to eachother.

7. The apparatus of claim 6 in which saidbody member includes springmeans operatively connected to said cam plate and normally urging saidcam edge portion out of engagement'with said cam follower.

8. The apparatus of claim 7 in which said spring means comprises a guideelement pivotally supported on said body memberv for movement inthesame'direction toward which the axis of rotation of said secondcutter member extends, and abutment element mounted on said guideelement and projecting laterally from said body member toward said camplate, said cam plate including a guide portion displaceably engaged Ion said abutment element.

9. The apparatus as set forth in claim 1 in which said slitter. assemblycomprises a carriage-yoke member connected to said means pivotally andreciprocably mounting said slitter assembly on said body member, amounting post mounted on said carriage-yoke member and dependingtherefrom, said second cutter means being journaled on a lower endportion of-said mounting post.

10. The apparatus as set forth in claim 9 in which said carriage-yokemember includes releasable fastening means extending transverselythroughsaid mounting-post for' adjustably'retaining said mounting-postthereon.

11. The apparatus as set forth in claim 10 in which said fastening meansextends transversely through said mounting-post forming an axis ofrotation thereat parallel to the axis of rotationof said second cuttingmeans.

12; The apparatus as set forth in claim 11 in which said carriage-yokemember includes. adjustable abutment means engaging one portion of saidmounting-post membet, and fixed abutment means disposed at an opposedportion of said mounting-post for pivotally adjusting said mounting-postin angular relationship with respect to the axis of rotation of saidfirst cutter means.

13. The apparatus as set forthin claim 9 in whichsaid carriage-yokemember includes a fixed abutment engaging one side of said mounting-postin spaced relation from the longitudinal axis thereof, and an adjustableabutment attain controlled cutting edge overlap.

References Cited by the Examiner UNITED STATES PATENTS 6/36 Thibedeau83-482 2,212,457 8/40 Schrier 83-482 2,571,201 10/51 Clenr 83-4822,897,893 8/59 Rockstrom 83-482 3,041,907 7/62 'Gallagher 83-504 X3,091,146 0 5/63 Bulk 83-482 X,

FOREIGN PATENTS 1,024,341 2/58 Germany.

ANDREW. R. JUHASZ, Primary Examiner.

1. APPARATUS FOR SLITTING A CONTINUOUS WEB OF MATERIAL COMPRISING ASUPPORT MEMBER, A BODY MEMBER MOUNTED ON SAID SUPPORT MEMBER, FIRSTCUTTER MEANS HAVING A CIRCULAR CUTTING EDGE AND MOUNTED BELOW SAID BODYMEMBER, A SLITTER ASSEMBLY INCLUDING A DEPENDING SECOND CUTTER MEANSHAVING A CIRCULAR CUTTING EDGE AND JOURNALED ON SAID SLITTER ASSEMBLY ONA FIXED AXIS OF ROTATION FOR DRIVING, SHEAR-ANGLE ENGAGEMENT WITH SAIDFIRST CUTTER MEANS, SAID SLITTER ASSEMBLY AND BODY MEMBER INCLUDINGMEANS PIVOTALLY AND RECIPROCABLY MOUNTING SAID SALITTER ASSEMBLY ON SAIDBODY MEMBER ON AN AXIS OF ROTATION OF SAID FIRST SUBSTANTIALLY NORMAL TOTHE AXIS OF ROTATION OF SAID FIRST CUTTER MEANS, FLUID MOTOR MEANS ONSAID BODY MEMBER OPERATIVELY CONNECTED TO SAID SLITTER ASSEMBLY FORCECIPROCATING SAID SLITTER ASSEMBLY AT SAID MEANS PIVOTALLY ANDRECIPROCABLY MOUNTING SAID SLITTER ASSEMBLY NORMALLY URGSAID SECONDCUTTER MEANS EDGE TOWARD SAID FIRST CUTTER MEANS EDGE, MEANS ON SAIDSLITTER ASSEMBLY NORMALLY URGING SAID SECOND CUTTER MEANS EDGE AWAY FROMFIRST CUTTER MEANS EDGE AND CAM MEANS ON SAID BODY MEMBER AND SAIDSLITTER ASSEMBLY AND INCLUDING CAMMING PORTIONS FOR PIVOTING SAIDSLITTER ASSEMBLY AND SAID SECOND CUTTER MEANS EDGE BODILY TOWARD ANDAWAY FROM SAID FIRST CUTTER MEANS EDGE DURING RECIPROCABLE MOVEMENT OFSAID SITTER ASSEMBLY DURING OPERATION OF SAID FLUID MOTOR MEANS.